EP1511947B2 - Gearshift transmission for a motor vehicle having a hydraulically actuatable multi-disc clutch - Google Patents

Gearshift transmission for a motor vehicle having a hydraulically actuatable multi-disc clutch Download PDF

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Publication number
EP1511947B2
EP1511947B2 EP03755924.2A EP03755924A EP1511947B2 EP 1511947 B2 EP1511947 B2 EP 1511947B2 EP 03755924 A EP03755924 A EP 03755924A EP 1511947 B2 EP1511947 B2 EP 1511947B2
Authority
EP
European Patent Office
Prior art keywords
clutch
bearing
transmission
gearshift
housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03755924.2A
Other languages
German (de)
French (fr)
Other versions
EP1511947B1 (en
EP1511947A1 (en
Inventor
Dieter Kraxner
Klaus Tiede
Wolfgang Grosspietsch
Paul Kraus
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dr Ing HCF Porsche AG
ZF Friedrichshafen AG
Original Assignee
Dr Ing HCF Porsche AG
ZF Sachs AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
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Application filed by Dr Ing HCF Porsche AG, ZF Sachs AG filed Critical Dr Ing HCF Porsche AG
Publication of EP1511947A1 publication Critical patent/EP1511947A1/en
Application granted granted Critical
Publication of EP1511947B1 publication Critical patent/EP1511947B1/en
Publication of EP1511947B2 publication Critical patent/EP1511947B2/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19228—Multiple concentric clutch shafts

Definitions

  • the invention relates to a gearbox for a motor vehicle with multiple clutch according to the features of the preamble of claim 1.
  • Task is therefore to improve the support or bearing of the coupling such that a Schwungradtapeleln prevented or mitigated or that a support effect for the crankshaft end is reached.
  • the coupling unit enclosing the clutch basket is supported on a housing cover of the clutch receiving housing.
  • the housing cover to a central opening through which a drive hub of the clutch basket is passed, a bearing flange on the outside of the clutch basket is supported or supported, wherein the clutch basket is closed by a drive hub receiving the clutch cover, which is bolted to the clutch basket ,
  • the clutch basket has a drive hub receiving the clutch cover, on the one hand bolted to the clutch basket and on the other hand, in its hub region has a bearing collar which is supported via a radial bearing on the bearing flange of Gescousedekkels.
  • the clutch basket in its axial extension to a rotary component for the oil supply of the coupling units, which is arranged coaxially to the outer gear shaft and radially supported by a fixed bearing in the clutch bell or in the gear housing and fixed axially.
  • three annular grooves are provided in an advantageous manner on the outer circumference of the rotary member, on the one hand, the oil supply of pressure chambers for the actuation of the two coupling units and on the other hand, a cooling oil supply for the clutch plates and an oil supply from the pressure chambers opposite pressure equalization chambers. Due to the fact that the oil supply via the rotary member takes place exclusively radially, oil seals adjacent to the rotary component are not or only slightly acted on by the oil pressure.
  • the outer and designed as a hollow shaft gear shaft is supported via a radial bearing in the rotary member, while the designed as a solid shaft inner gear shaft also supported on the outer gear shaft via a radial bearing, which is housed in a formed in the solid shaft ring groove.
  • the screwed to the clutch bell or on the gear housing cover forms a good bearing base for the multiple clutch by a simple centering of the bearing seats for the provided on the rotary member fixed bearing and provided on the bearing flange of the housing cover radial bearings to each other.
  • a double clutch 6 consisting of two clutch units 2 and 4 is arranged in a housing, hereinafter referred to as bell housing 1.
  • the bell housing 1 can be arranged as a separate component in a drive train of an internal combustion engine between the engine and transmission or, alternatively, be integrally formed out of the gear housing.
  • two transmission input shafts 8 and 10 are received, which cooperate in a known manner with the two coupling units 2 and 4 for the mutual switching of a first and second group of transmission gears.
  • the double clutch 6 is sealed oil-tight by a separate housing cover 12, which is bolted to the GeHouseglokke 1 and sealed.
  • the housing cover 12 at its radial outer end on a collar 16, in which a groove 14 is provided for receiving a sealing ring.
  • a central opening 18 is provided, through which a drive hub 20 of a clutch basket 22 of the double clutch 6 is passed.
  • the drive hub 20 has an external toothing 24, which engages in the internal toothing of a torsional vibration damper 26.
  • the integrated in a dual mass flywheel torsional vibration damper is screwed with its primary side 27 on the crankshaft end 28 of the engine unit, not shown.
  • the central opening 18 is bounded by an out of the housing cover 12 formed and inwardly directed bearing flange 30, on the outside of the clutch basket 22 is supported on the engine side via a radial bearing 32, the latter being formed in the present embodiment as a rolling bearing; Alternatively, a plain bearing design is possible.
  • the clutch basket 22 has a bearing collar 34 provided with a clutch cover 36 which is fastened via screws 38 on the clutch basket 22 is.
  • the clutch basket 22 is the transmission side extended by a rotary member 40 which surrounds the outer transmission input shaft coaxial and rotatable thereto.
  • the rotary member 40 and the clutch basket 22 is supported at its gear-side end via a ball bearing 42 in the bell housing 1, wherein the ball bearing 42 is received in a cylindrically shaped neck portion 44 of the bell housing 1 and clamped in both axial directions.
  • the ball bearing 42 is received on the gear side facing in a stepped bore of the neck portion 44 and is axially secured on the other side via a thrust washer 46.
  • the thrust washer 46 is in turn secured by a snap ring 48 arranged in an internal groove of the cylindrical neck portion 44.
  • a left-aligned and a right-aligned stop 48 and 50 are provided on the rotary member 40 to the left and right of the ball bearing 42.
  • the flush-mounted stop 50 is in turn formed by a snap ring, which is inserted in a arranged on the outer circumference of the rotary member 40 circumferential groove.
  • the bell housing 1 is closed at the end face of the cylindrical neck portion 44 by a second housing cover 52, which is screwed to the neck portion 44 and sealed by a 0 - ring 54 relative to the bell housing 1.
  • the two through the housing cover 52 passed through gear shafts 8 and 10 are sealed by a shaft seal 56.
  • the rotary member 40 has on its outer circumference three annular grooves 58, 60 and 62, over which, as explained in more detail later, the oil is supplied to the coupling units 2 and 4.
  • the three annular grooves are sealed against each other by piston rings, which are inserted into correspondingly provided annular grooves 64, 66, 68 and 70.
  • a bush 72 provided with oil supply openings 71 is inserted between the rotary component 40 and the opening of the cylindrical neck portion 44.
  • the outer transmission input shaft 10 is supported relative to the rotary member 40 of the clutch basket 22 by a trained as a needle bearing 74 radial bearing. Trained as a solid shaft inner transmission input shaft 8 is supported via a radial bearing 76 relative to the formed as a hollow shaft outer transmission input shaft 10.
  • the radial bearing 76 is inserted in a formed in the solid shaft 8 annular groove;
  • the shaft sealing ring 78 arranged at the front end of the hollow shaft 10 can be dimensioned smaller in its outer circumference.
  • the shaft seal 78 serves to seal the guided between the hollow shaft 10 and the solid shaft 8 gear oil, the u. a. for lubrication of the radial bearing 76 is required.
  • journal-shaped end 80 of the solid shaft 8 relative to the drive hub 20 may be supported by a trained as a needle bearing radial bearing 82.
  • a shaft sealing ring 84 is provided between the inside of the bearing flange 30 and the outside of the drive hub 20.
  • Both coupling units 2 and 4 have a plurality of disk plates designed as lamellae, which are arranged one behind the other alternately as driving external toothed friction plates 86 and as driven internal toothed lamellae 88.
  • the externally toothed friction plates, referred to below as outer plates 86, of the coupling unit 2 engage in grooves 90 of the coupling basket 22;
  • the externally toothed friction plates 86 engage the coupling unit 4 in grooves 92 of an integrally connected to the rotary member 40 of the clutch basket 22 outer disk carrier 94 a.
  • the driven internal toothed disks are each assigned to an inner disk carrier 96 or 98.
  • the inner disk carrier 96 of the coupling unit 2 is rotatably connected via a toothing 100 with the solid shaft 8, while the inner disk carrier 98 of the coupling unit 4 via a toothing 102 rotatably connected to the hollow shaft 10 is connected.
  • actuating piston 104 and 106 are arranged, which press the outer plates 86 against the inner plates 88 via a corresponding Druckölbeetzschung.
  • a pressure chamber 108 is formed, which is sealed by means of corresponding sealing elements 110 and 112.
  • a pressure chamber 114 is provided for the actuating piston 106, which is also sealed by sealing elements 116 and 118.
  • the pressure chamber 108 is supplied with oil via the annular groove 58 and an axial bore 124 provided in the rotary component 40, while the pressure chamber 114 is supplied with oil via the annular groove 62 and an axial bore 126.
  • the two pressure chambers 108 and 114 are each a pressure compensation chamber 128 and 130 opposite, which are supplied via the annular groove 60 and via a third in the rotary member 40 arranged axial bore (not shown) with oil.
  • centrifugal force due to the engagement movement of the two actuating pistons 104 and 106 are affected; by the pressure compensation chambers 128 and 130, a corresponding compensation of the force exerted on the piston centrifugal force forces is achieved.
  • the pressure compensation chambers 128, 130 are in turn sealed by sealing elements 112 and 131, the sealing element 112 having two sealing lips 112a and 112b; Sealing lip 112a seals the pressure chamber 108, while sealing lip 112b seals the pressure compensation chamber 128.
  • the pressure compensation chamber 130 is bounded by a wall portion 132 in which an opening 134 is arranged. Via the opening 134, the oil in the pressure compensation chamber 130 for cooling the fins 86, 88 can pass into the coupling space.
  • a sliding bearing 136 is provided between the clutch cover 36 and the inner disk carrier 96 for the axial support of both components; Similarly, between the inner disk carrier 96 of the coupling unit 2 and the inner disk carrier 98 of the coupling unit 4, a needle bearing 138 and between the inner disk carrier 98 and the wall portion 132, a sliding bearing 140 is provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Mechanical Operated Clutches (AREA)
  • General Details Of Gearings (AREA)

Description

Die Erfindung geht aus von einem Gangschaltgetriebe für ein Kraftfahrzeug mit Mehrfachkupplung gemäß den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a gearbox for a motor vehicle with multiple clutch according to the features of the preamble of claim 1.

Aus der DE 100 04 190 A1 ist eine Mehrfach - Kupplungseinrichtung bekannt, bei der die Kupplung bzw. der beide Kupplungseinheiten aufnehmende Kupplungskorb an den beiden Getriebeeingangswellen axial und radial gelagert ist. Hierdurch wird erreicht, dass die Toleranzen, die das Getriebegehäuse im Bereich der Gehäuseglocke und die Kupplungseinrichtung erfüllen müssen, weniger streng sind. Hier besteht jedoch die Gefahr, dass bei einer derartigen Abstützung der Kupplung ein Taumeln des am Kurbelwellenende befestigten Schwungrades sich auf die Kupplung überträgt. Auch aus der US 4,463,621 ist ein gattungsgemäßes Gangschaltgetriebe bekannt, das darüber hinaus an einem Gehäusedeckel einen Lagerflansch aufweist. Auch dieses Gangschaltgetriebe besitzt den beschriebenen Nachteil.From the DE 100 04 190 A1 a multiple clutch device is known, in which the clutch or both coupling units receiving clutch basket is mounted axially and radially on the two transmission input shafts. This ensures that the tolerances that must meet the gear housing in the bell housing and the coupling device, are less strict. However, there is a risk here that in such a support of the clutch, a tumbling of the flywheel attached to the crankshaft end transmits to the clutch. Also from the US 4,463,621 is a generic gearshift known, which also has a bearing flange on a housing cover. Also, this gearbox has the described disadvantage.

Aufgabe ist es daher, die Abstützung bzw. Lagerung der Kupplung derart zu verbessern, dass ein Schwungradtaumeln verhindert oder abgeschwächt bzw. das eine Stützwirkung für das Kurbelwellenende erreichbar ist.Task is therefore to improve the support or bearing of the coupling such that a Schwungradtapeleln prevented or mitigated or that a support effect for the crankshaft end is reached.

Die Lösung der Aufgabe erfolgt durch die im Anspruch 1 angegebenen Merkmale.The solution of the problem is achieved by the features specified in claim 1.

Es ist erfindungsgemäß vorgesehen, dass der die Kupplungseinheiten umschließende Kupplungskorb an einem Gehäusedeckel des die Kupplung aufnehmenden Gehäuses abgestützt ist. Dazu weist der Gehäusedeckel um eine zentrale Öffnung, durch die eine Antriebsnabe des Kupplungskorbes hindurchgeführt ist, einen Lagerflansch auf, an dessen Außenseite der Kupplungskorb gelagert bzw. abgestützt ist, wobei der Kupplungskorb durch einen die Antriebsnabe aufnehmenden Kupplungsdeckel verschlossen ist, der am Kupplungskorb verschraubt ist.It is inventively provided that the coupling unit enclosing the clutch basket is supported on a housing cover of the clutch receiving housing. For this purpose, the housing cover to a central opening through which a drive hub of the clutch basket is passed, a bearing flange on the outside of the clutch basket is supported or supported, wherein the clutch basket is closed by a drive hub receiving the clutch cover, which is bolted to the clutch basket ,

In den Unteransprüchen sind weitere vorteilhafte Ausgestaltungen und Verbesserungen des erfindungsgemäßen Gangschaltgetriebes enthalten.In the subclaims further advantageous refinements and improvements of the inventive gearshift transmission are included.

Der Kupplungskorb weist einen die Antriebsnabe aufnehmenden Kupplungsdeckel auf, der einerseits am Kupplungskorb verschraubt und andererseits in seinem Nabenbereich einen Lagerkragen aufweist, der über ein Radiallager am Lagerflansch des Gehäusedekkels abgestützt ist.The clutch basket has a drive hub receiving the clutch cover, on the one hand bolted to the clutch basket and on the other hand, in its hub region has a bearing collar which is supported via a radial bearing on the bearing flange of Gehäusedekkels.

Darüber hinaus weist der Kupplungskorb in seiner axialen Verlängerung ein Drehbauteil für die Ölversorgung der Kupplungseinheiten auf, das koaxial zur äußeren Getriebewelle angeordnet und über ein Festlager in der Kupplungsglocke bzw. im Getriebegehäuse radial abgestützt und axial festgelegt ist.In addition, the clutch basket in its axial extension to a rotary component for the oil supply of the coupling units, which is arranged coaxially to the outer gear shaft and radially supported by a fixed bearing in the clutch bell or in the gear housing and fixed axially.

Für die Ölzuführung sind auf vorteilhafte Art und Weise am Außenumfang des Drehbauteils drei Ringnuten vorgesehen, über die einerseits die Ölversorgung von Druckkammern für die Betätigung der beiden Kupplungseinheiten und andererseits eine Kühlölversorgung für die Kupplungslamellen sowie eine Ölversorgung von den Druckkammern gegenüber liegenden Druckausgleichskammern erfolgt. Dadurch, dass die Ölzufuhr über das Drehbauteil ausschließlich radial erfolgt, werden an das Drehbauteil angrenzende Wellendichtringe nicht oder nur geringfügig durch den Öldruck beaufschlagt.For the oil supply three annular grooves are provided in an advantageous manner on the outer circumference of the rotary member, on the one hand, the oil supply of pressure chambers for the actuation of the two coupling units and on the other hand, a cooling oil supply for the clutch plates and an oil supply from the pressure chambers opposite pressure equalization chambers. Due to the fact that the oil supply via the rotary member takes place exclusively radially, oil seals adjacent to the rotary component are not or only slightly acted on by the oil pressure.

Die äußere und als Hohlwelle ausgebildete Getriebewelle ist über ein Radiallager im Drehbauteil abgestützt, während sich die als Vollwelle ausgebildete innere Getriebewelle an der äußeren Getriebewelle ebenfalls über ein Radiallager abstützt, das in einer in der Vollwelle ausgebildeten Ringnut Aufnahme findet.The outer and designed as a hollow shaft gear shaft is supported via a radial bearing in the rotary member, while the designed as a solid shaft inner gear shaft also supported on the outer gear shaft via a radial bearing, which is housed in a formed in the solid shaft ring groove.

Der an der Kupplungsglocke bzw. am Getriebegehäuse verschraubte Gehäusedeckel bildet eine gute Lagerbasis für die Mehrfachkupplung durch eine einfache Zentrierung der Lagersitze für das am Drehbauteil vorgesehene Festlager und das am Lagerflansch des Gehäusedeckels vorgesehene Radiallager zueinander.The screwed to the clutch bell or on the gear housing cover forms a good bearing base for the multiple clutch by a simple centering of the bearing seats for the provided on the rotary member fixed bearing and provided on the bearing flange of the housing cover radial bearings to each other.

Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Beschreibung und Zeichnung näher erläutert.An embodiment of the invention is explained in more detail in the following description and drawings.

Diese zeigt in der einzigen Figur einen Längsschnitt durch ein Gangschaltgetriebe im Kupplungsbereich.This shows in the single figure a longitudinal section through a gearbox in the clutch area.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In einem Gehäuse, im folgenden als Gehäuseglocke 1 bezeichnet, ist eine aus zwei Kupplungseinheiten 2 und 4 bestehende Doppelkupplung 6 angeordnet. Die Gehäuseglocke 1 kann dabei als separates Bauteil in einem Antriebsstrang einer Brennkraftmaschine zwischen Motor und Getriebe angeordnet oder alternativ dazu, einstückig aus dem Getriebegehäuse herausgebildet sein. In der Doppelkupplung 6 sind zwei Getriebeeingangswellen 8 und 10 aufgenommen, die auf bekannte Art und Weise mit den beiden Kupplungseinheiten 2 und 4 zum wechselseitigen Schalten einer ersten und zweiten Gruppe von Getriebegängen zusammenwirken. Die Doppelkupplung 6 ist öldicht durch einen separaten Gehäusedeckel 12 verschlossen, der an der Gehäuseglokke 1 verschraubt und abgedichtet ist. Dazu weist der Gehäusedeckel 12 an seinem radialen äußeren Ende einen Kragen 16 auf, in der eine Nut 14 zur Aufnahme eines Dichtungsringes vorgesehen ist. Im Gehäusedeckel 12 ist eine zentrale Öffnung 18 vorgesehen, durch die eine Antriebsnabe 20 eines Kupplungskorbes 22 der Doppelkupplung 6 hindurchgeführt ist. Die Antriebsnabe 20 weist eine Außenverzahnung 24 auf, die in die Innenverzahnung eines Torsionsschwingungsdämpfer 26 eingreift. Der in einem Zweimassenschwungrad integrierte Torsionsschwingungsdämpfer, dessen Aufbau bekannt ist und hier nicht näher beschrieben wird, ist mit seiner Primärseite 27 am Kurbelwellenende 28 der nicht näher dargestellten Motoreinheit verschraubt.In a housing, hereinafter referred to as bell housing 1, a double clutch 6 consisting of two clutch units 2 and 4 is arranged. The bell housing 1 can be arranged as a separate component in a drive train of an internal combustion engine between the engine and transmission or, alternatively, be integrally formed out of the gear housing. In the dual clutch 6, two transmission input shafts 8 and 10 are received, which cooperate in a known manner with the two coupling units 2 and 4 for the mutual switching of a first and second group of transmission gears. The double clutch 6 is sealed oil-tight by a separate housing cover 12, which is bolted to the Gehäuseglokke 1 and sealed. For this purpose, the housing cover 12 at its radial outer end on a collar 16, in which a groove 14 is provided for receiving a sealing ring. In the housing cover 12, a central opening 18 is provided, through which a drive hub 20 of a clutch basket 22 of the double clutch 6 is passed. The drive hub 20 has an external toothing 24, which engages in the internal toothing of a torsional vibration damper 26. The integrated in a dual mass flywheel torsional vibration damper, the structure of which is known and will not be described in detail here, is screwed with its primary side 27 on the crankshaft end 28 of the engine unit, not shown.

Die zentrale Öffnung 18 wird durch einen aus dem Gehäusedeckel 12 herausgebildeten und nach innen gerichteten Lagerflansch 30 begrenzt, an dessen Außenseite der Kupplungskorb 22 motorseitig über ein Radiallager 32 abgestützt ist, wobei letzteres im vorliegenden Ausführungsbeispiel als Wälzlager ausgebildet ist; alternativ dazu ist auch eine Gleitlager-Ausführung möglich. Dazu weist der Kupplungskorb 22 einen mit einem Lagerkragen 34 versehenen Kupplungsdeckel 36 auf, der über Schrauben 38 am Kupplungskorb 22 befestigt ist.The central opening 18 is bounded by an out of the housing cover 12 formed and inwardly directed bearing flange 30, on the outside of the clutch basket 22 is supported on the engine side via a radial bearing 32, the latter being formed in the present embodiment as a rolling bearing; Alternatively, a plain bearing design is possible. For this purpose, the clutch basket 22 has a bearing collar 34 provided with a clutch cover 36 which is fastened via screws 38 on the clutch basket 22 is.

Der Kupplungskorb 22 ist getriebeseitig durch ein Drehbauteil 40 verlängert, das die äußere Getriebeeingangswelle koaxial und drehbeweglich dazu umschließt. Das Drehbauteil 40 bzw. der Kupplungskorb 22 ist an seinem getriebeseitigen Ende über ein Kugellager 42 in der Gehäuseglocke 1 abgestützt, wobei das Kugellager 42 in einem zylinderförmig ausgebildeten Halsabschnitt 44 der Gehäuseglocke 1 aufgenommen und in beide axiale Richtungen eingespannt bzw. festgelegt ist. Dazu ist das Kugellager 42 auf der dem Getriebe zugewandten Seite in einer Stufenbohrung des Halsabschnittes 44 aufgenommen und wird auf der andere Seite über eine Anlaufscheibe 46 axial gesichert. Die Anlaufscheibe 46 wird wiederum durch einen in einer Innennut des zylinderförmigen Halsabschnittes 44 angeordneten Sprengring 48 gesichert. Gleichzeitig ist das Drehbauteil 40 gegenüber dem Kugellager 42 gegen axiale Verschiebung gesichert; dazu ist auf dem Drehbauteil 40 links und rechts des Kugellagers 42 ein linksbündiger und ein rechtsbündiger Anschlag 48 und 50 vorgesehen. Der rechtsbündige Anschlag 50 wird wiederum durch einen Sprengring gebildet, der in einer auf dem Außenumfang des Drehbauteils 40 angeordneten umlaufenden Nut eingesetzt ist.The clutch basket 22 is the transmission side extended by a rotary member 40 which surrounds the outer transmission input shaft coaxial and rotatable thereto. The rotary member 40 and the clutch basket 22 is supported at its gear-side end via a ball bearing 42 in the bell housing 1, wherein the ball bearing 42 is received in a cylindrically shaped neck portion 44 of the bell housing 1 and clamped in both axial directions. For this purpose, the ball bearing 42 is received on the gear side facing in a stepped bore of the neck portion 44 and is axially secured on the other side via a thrust washer 46. The thrust washer 46 is in turn secured by a snap ring 48 arranged in an internal groove of the cylindrical neck portion 44. At the same time the rotary member 40 is secured against axial displacement relative to the ball bearing 42; For this purpose, a left-aligned and a right-aligned stop 48 and 50 are provided on the rotary member 40 to the left and right of the ball bearing 42. The flush-mounted stop 50 is in turn formed by a snap ring, which is inserted in a arranged on the outer circumference of the rotary member 40 circumferential groove.

Getriebeseitig wird die Gehäuseglocke 1 an der Stirnseite des zylinderförmigen Halsabschnittes 44 durch einen zweiten Gehäusedeckel 52 abgeschlossen, der am Halsabschnitt 44 verschraubt und über einen 0 - Ring 54 gegenüber der Gehäuseglocke 1 abgedichtet ist. Die beiden durch den Gehäusedeckel 52 hindurchgeführten Getriebewellen 8 und 10 sind über einen Wellendichtring 56 abgedichtet.On the transmission side, the bell housing 1 is closed at the end face of the cylindrical neck portion 44 by a second housing cover 52, which is screwed to the neck portion 44 and sealed by a 0 - ring 54 relative to the bell housing 1. The two through the housing cover 52 passed through gear shafts 8 and 10 are sealed by a shaft seal 56.

Das Drehbauteil 40 weist an seinem Außenumfang drei Ringnuten 58, 60 und 62 auf, über die, wie noch später näher erläutert, die Ölzufuhr zu den Kupplungseinheiten 2 und 4 erfolgt. Die drei Ringnuten sind durch Kolbenringe gegeneinander abgedichtet, die in entsprechend dafür vorgesehene Ringnuten 64, 66, 68 und 70 eingelegt sind. Im Bereich der Ölzufuhr ist zwischen dem Drehbauteil 40 und der Öffnung des zylinderförmigen Halsabschnittes 44 eine mit Öl - Zufuhröffnungen 71 versehene Buchse 72 eingesetzt.The rotary member 40 has on its outer circumference three annular grooves 58, 60 and 62, over which, as explained in more detail later, the oil is supplied to the coupling units 2 and 4. The three annular grooves are sealed against each other by piston rings, which are inserted into correspondingly provided annular grooves 64, 66, 68 and 70. In the area of the oil supply, a bush 72 provided with oil supply openings 71 is inserted between the rotary component 40 and the opening of the cylindrical neck portion 44.

Die äußere Getriebeeingangswelle 10 ist gegenüber dem Drehbauteil 40 des Kupplungskorbes 22 durch ein als Nadellager 74 ausgebildetes Radiallager abgestützt. Die als Vollwelle ausgebildete innere Getriebeeingangswelle 8 ist über ein Radiallager 76 gegenüber der als Hohlwelle ausgebildeten äußeren Getriebeeingangswelle 10 abgestützt. Das Radiallager 76 ist dabei in einer in der Vollwelle 8 ausgebildeten Ringnut eingesetzt; dadurch ist der am stirnseitigen Ende der Hohlwelle 10 angeordnete Wellendichtring 78 in seinem Außenumfang kleiner dimensionierbar. Der Wellendichtring 78 dient der Abdichtung des zwischen der Hohlwelle 10 und der Vollwelle 8 geführten Getriebeöls, das u. a. zur Schmierung des Radiallagers 76 erforderlich ist. Alternativ oder zusätzlich zur Abstützung der Getriebeeingangswellen 8, 10 im Kupplungskorb 22 durch das Radiallager 74 kann das zapfenförmige Ende 80 der Vollwelle 8 gegenüber der Antriebsnabe 20 durch ein als Nadellager ausgebildetes Radiallager 82 abgestützt sein. Zur Abdichtung der Antriebsnabe 20 gegenüber dem Gehäusedeckel 12 ist zwischen der Innenseite des Lagerflansches 30 und der Außenseite der Antriebsnabe 20 ein Wellendichtring 84 vorgesehen.The outer transmission input shaft 10 is supported relative to the rotary member 40 of the clutch basket 22 by a trained as a needle bearing 74 radial bearing. Trained as a solid shaft inner transmission input shaft 8 is supported via a radial bearing 76 relative to the formed as a hollow shaft outer transmission input shaft 10. The radial bearing 76 is inserted in a formed in the solid shaft 8 annular groove; As a result, the shaft sealing ring 78 arranged at the front end of the hollow shaft 10 can be dimensioned smaller in its outer circumference. The shaft seal 78 serves to seal the guided between the hollow shaft 10 and the solid shaft 8 gear oil, the u. a. for lubrication of the radial bearing 76 is required. Alternatively or in addition to the support of the transmission input shafts 8, 10 in the clutch basket 22 by the radial bearing 74, the journal-shaped end 80 of the solid shaft 8 relative to the drive hub 20 may be supported by a trained as a needle bearing radial bearing 82. For sealing the drive hub 20 relative to the housing cover 12, a shaft sealing ring 84 is provided between the inside of the bearing flange 30 and the outside of the drive hub 20.

Der Aufbau und die Wirkungsweise der beiden im Kupplungskorb 22 angeordneten Kupplungseinheiten 2 und 4 ist beispielsweise aus der DE 100 04 190 A1 bekannt und wird daher im folgendenden nur soweit erforderlich, in ihrem Aufbau näher beschrieben. Beide Kupplungseinheiten 2 und 4 weisen mehrere als Lamellen ausgebildete Kupplungsscheiben auf, die hintereinander im Wechsel als treibende außenverzahnte Reiblamellen 86 und als getriebene innenverzahnte Lamellen 88 angeordnet sind. Die außenverzahnten Reiblamellen, im folgenden als Außenlamellen 86 bezeichnet, der Kupplungseinheit 2 greifen in Nuten 90 des Kupplungskorbes 22 ein; analog dazu greifen die außenverzahnten Reiblamellen 86 der Kupplungseinheit 4 in Nuten 92 eines einstückig mit dem Drehbauteil 40 des Kupplungskorbes 22 verbundenen Außenlamellenträgers 94 ein. Die getriebenen innenverzahnten Lamellen, im folgenden als Innenlamellen 88 bezeichnet, sind jeweils einem Innenlamellenträger 96 bzw. 98 zugeordnet. Der Innenlamellenträger 96 der Kupplungseinheit 2 ist über eine Verzahnung 100 drehfest mit der Vollwelle 8 verbunden, während der Innenlamellenträger 98 der Kupplungseinheit 4 über eine Verzahnung 102 drehfest mit der Hohlwelle 10 verbunden ist.The structure and operation of the two arranged in the clutch basket 22 coupling units 2 and 4 is for example from the DE 100 04 190 A1 is known and will therefore in the following only as necessary, described in detail in their construction. Both coupling units 2 and 4 have a plurality of disk plates designed as lamellae, which are arranged one behind the other alternately as driving external toothed friction plates 86 and as driven internal toothed lamellae 88. The externally toothed friction plates, referred to below as outer plates 86, of the coupling unit 2 engage in grooves 90 of the coupling basket 22; Similarly, the externally toothed friction plates 86 engage the coupling unit 4 in grooves 92 of an integrally connected to the rotary member 40 of the clutch basket 22 outer disk carrier 94 a. The driven internal toothed disks, referred to below as inner disks 88, are each assigned to an inner disk carrier 96 or 98. The inner disk carrier 96 of the coupling unit 2 is rotatably connected via a toothing 100 with the solid shaft 8, while the inner disk carrier 98 of the coupling unit 4 via a toothing 102 rotatably connected to the hollow shaft 10 is connected.

An den beiden außenverzahnten Endlamellen 86 der beiden Kupplungseinheiten 2 und 4 sind Betätigungskolben 104 und 106 angeordnet, die über eine entsprechende Druckölbeaufschlagung die Außenlamellen 86 gegen die Innenlamellen 88 pressen. Zur Druckbeaufschlagung für die Kupplungseinheit 2 ist eine Druckkammer 108 ausgebildet, die über entsprechende Dichtungselemente 110 und 112 abgedichtet ist. Analog dazu ist für den Betätigungskolben 106 eine Druckkammer 114 vorgesehen, die ebenfalls über Dichtungselemente 116 und 118 abgedichtet ist. Im nicht eingerückten Zustand der beiden Kupplungseinheiten 2 und 4 werden die Betätigungskolben 104 und 106 über entsprechende Membranfedern 120, 122 gegen den Kupplungskorb 22 bzw. gegen den Lamellenträger 94 gedrückt.On the two externally toothed end plates 86 of the two coupling units 2 and 4 actuating piston 104 and 106 are arranged, which press the outer plates 86 against the inner plates 88 via a corresponding Druckölbeaufschlagung. For pressurizing the coupling unit 2, a pressure chamber 108 is formed, which is sealed by means of corresponding sealing elements 110 and 112. Similarly, a pressure chamber 114 is provided for the actuating piston 106, which is also sealed by sealing elements 116 and 118. When the two coupling units 2 and 4 are not in the engaged state, the actuating pistons 104 and 106 are pressed against the clutch basket 22 or against the disk carrier 94 via corresponding diaphragm springs 120, 122.

Über die Ringnut 58 und eine im Drehbauteil 40 vorgesehene Axialbohrung 124 wird die Druckkammer 108 mit Öl versorgt, während über die Ringnut 62 und eine Axialbohrung 126 die Druckkammer 114 mit Öl versorgt wird. Den beiden Druckkammern 108 und 114 liegen jeweils eine Druckausgleichskammer 128 und 130 gegenüber, die über die Ringnut 60 und über eine dritte im Drehbauteil 40 angeordnete Axialbohrung (nicht dargestellt) mit Öl versorgt werden. Bei höheren Drehzahlen kann fliehkraftbedingt die Einrückbewegung der beiden Betätigungskolben 104 und 106 beeinträchtigt werden; durch die Druckausgleichskammern 128 und 130 wird eine entsprechende Kompensation der auf den Kolben ausgeübten fliehkraftbedingten Druckkräfte erreicht. Die Druckausgleichskammern 128, 130 sind wiederrum durch Dichtungselemente 112 und 131 abgedichtet, wobei das Dichtungselement 112 zwei Dichtlippen 112a und 112b aufweist; Dichtlippe 112a dichtet die Druckkammer 108 ab, während Dichtlippe 112b die Druckausgleichskammer 128 abdichtet. Die Druckausgleichskammer 130 ist durch ein Wandungsteil 132 begrenzt, in dem eine Öffnung 134 angeordnet ist. Über die Öffnung 134 kann das in der Druckausgleichskammer 130 befindliche Öl zur Kühlung der Lamellen 86, 88 in den Kupplungsraum übertreten.The pressure chamber 108 is supplied with oil via the annular groove 58 and an axial bore 124 provided in the rotary component 40, while the pressure chamber 114 is supplied with oil via the annular groove 62 and an axial bore 126. The two pressure chambers 108 and 114 are each a pressure compensation chamber 128 and 130 opposite, which are supplied via the annular groove 60 and via a third in the rotary member 40 arranged axial bore (not shown) with oil. At higher speeds centrifugal force due to the engagement movement of the two actuating pistons 104 and 106 are affected; by the pressure compensation chambers 128 and 130, a corresponding compensation of the force exerted on the piston centrifugal force forces is achieved. The pressure compensation chambers 128, 130 are in turn sealed by sealing elements 112 and 131, the sealing element 112 having two sealing lips 112a and 112b; Sealing lip 112a seals the pressure chamber 108, while sealing lip 112b seals the pressure compensation chamber 128. The pressure compensation chamber 130 is bounded by a wall portion 132 in which an opening 134 is arranged. Via the opening 134, the oil in the pressure compensation chamber 130 for cooling the fins 86, 88 can pass into the coupling space.

Zwischen dem Kupplungsdeckel 36 und dem Innenlamellenträger 96 ist zur axialen Abstützung beider Bauteile ein Gleitlager 136 vorgesehen; analog dazu ist zwischen dem Innenlamellenträger 96 der Kupplungseinheit 2 und dem Innenlamellenträger 98 der Kupplungseinheit 4 ein Nadellager 138 sowie zwischen dem Innenlamellenträger 98 und dem Wandungsteil 132 ein Gleitlager 140 vorgesehen.Between the clutch cover 36 and the inner disk carrier 96, a sliding bearing 136 is provided for the axial support of both components; Similarly, between the inner disk carrier 96 of the coupling unit 2 and the inner disk carrier 98 of the coupling unit 4, a needle bearing 138 and between the inner disk carrier 98 and the wall portion 132, a sliding bearing 140 is provided.

Claims (9)

  1. Gearshift transmission for a motor vehicle having a hydraulically actuable multi-disc clutch, in particular dual clutch, having a first transmission input shaft (8) for driving a first group of transmission gears and having a second transmission input shaft (10) for driving a second group of transmission gears, with the two transmission input shafts (8, 10) being assigned in each case one clutch unit (2, 4) and with the two transmission input shafts (8, 10) and the two clutch units (2, 4) being arranged coaxially with respect to one another, and having a stationary housing (1) which holds the two clutch units (2, 4) and which can be closed off at the end side by a housing cover (12) and which has a central opening (18) through which a drive hub of a clutch cage (22) extends, characterized in that the housing cover (12) has, around the central opening (18), a bearing flange (30) on the outside of which the clutch cage (22) is mounted or supported, clutch cage (22) is closed off by a clutch cover (36) which holds the drive hub (20) and which is screwed to the clutch cage (22).
  2. Gearshift transmission according to Claim 1, characterized in that the clutch cover (36) has a bearing collar (34) which is supported via a first radial bearing (32) on the bearing flange (30) of the housing cover (12).
  3. Gearshift transmission according to one of the preceding claims, characterized in that the clutch cage (22) has, in the axial elongation thereof, a rotary component (40) for the supply of oil, which rotary component (40) is arranged coaxially with respect to the outer transmission shaft and is radially supported and axially secured by means of a fixed bearing (42) in the housing (1).
  4. Gearshift transmission according to Claim 3, characterized in that the fixed bearing has a ball bearing (42) which is clamped axially in the housing (1).
  5. Gearshift transmission according to Claim 3 or 4, characterized in that three encircling annular grooves (58, 60, 62) are provided on the outer circumference of the rotary component (40), which annular grooves (58, 60, 62) serve to supply oil for the actuation of the two clutch units (2, 4) and to supply cooling oil to the clutch units (2, 4) which are provided with discs (86, 88).
  6. Gearshift transmission according to one of the preceding claims, characterized in that the inner transmission shaft (8) has an annular groove in which is held a second radial bearing (76) for support with respect to the outer transmission shaft (10).
  7. Gearshift transmission according to one of Claims 3 to 6, characterized in that the outer transmission shaft (10) is supported in the rotary component (40) by means of a third radial bearing (74).
  8. Gearshift transmission according to Claim 1, characterized in that a shaft sealing ring (84) is provided between the inner side of the bearing flange (30) and the outer side of the drive hub (20) of the clutch cage (22).
  9. Gearshift transmission according to Claim 1, characterized in that the housing cover (12) is screwed to the housing (1) and is sealed off to the outside by means of an O-ring seal (14).
EP03755924.2A 2002-05-29 2003-03-26 Gearshift transmission for a motor vehicle having a hydraulically actuatable multi-disc clutch Expired - Lifetime EP1511947B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10223780A DE10223780C1 (en) 2002-05-29 2002-05-29 Gear shift mechanism, for an IC motor with a multiple hydraulic clutch, has a bearing flange around the gear housing opening as a support for the roller bearing between it and the clutch cage with the drive hub
DE10223780 2002-05-29
PCT/EP2003/003108 WO2003102438A1 (en) 2002-05-29 2003-03-26 Gearshift transmission for a motor vehicle having a hydraulically actuatable multi-disc clutch

Publications (3)

Publication Number Publication Date
EP1511947A1 EP1511947A1 (en) 2005-03-09
EP1511947B1 EP1511947B1 (en) 2010-03-03
EP1511947B2 true EP1511947B2 (en) 2017-03-15

Family

ID=28051329

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Application Number Title Priority Date Filing Date
EP03755924.2A Expired - Lifetime EP1511947B2 (en) 2002-05-29 2003-03-26 Gearshift transmission for a motor vehicle having a hydraulically actuatable multi-disc clutch

Country Status (6)

Country Link
US (1) US7147095B2 (en)
EP (1) EP1511947B2 (en)
JP (1) JP4473118B2 (en)
KR (1) KR100901608B1 (en)
DE (2) DE10223780C1 (en)
WO (1) WO2003102438A1 (en)

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KR101786805B1 (en) 2016-04-18 2017-11-16 씨스톤 테크놀로지스(주) Actuator for dual clutch
DE102017206221B4 (en) 2017-04-11 2022-12-22 Zf Friedrichshafen Ag Multiple clutch assembly, dual clutch transmission assembly and motor vehicle
DE102018203073A1 (en) * 2018-03-01 2019-09-05 Zf Friedrichshafen Ag Drive arrangement for a rail vehicle
FR3082253B1 (en) * 2018-06-07 2021-11-19 Valeo Embrayages TORQUE TRANSMISSION DEVICE
DE102021203150B3 (en) 2021-03-29 2022-09-01 Magna Pt B.V. & Co. Kg multiple clutch assembly

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EP0185176A1 (en) † 1984-12-20 1986-06-25 Dr.Ing.h.c. F. Porsche Aktiengesellschaft Double clutch for a motor vehicle transmission
DE3615367C2 (en) † 1986-05-06 1989-12-28 Getrag Getriebe- Und Zahnradfabrik Gmbh, 7140 Ludwigsburg, De
US6116398A (en) † 1996-03-19 2000-09-12 Exedy Corporation Multi-plate dry clutch having hub movement limiting means
EP1043512B1 (en) † 1999-04-05 2008-08-20 General Motors Corporation Rotating clutch balance apparatus
EP1174631A2 (en) † 2000-07-17 2002-01-23 Mannesmann Sachs Aktiengesellschaft Multiple clutch device
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EP1412650A1 (en) † 2001-07-31 2004-04-28 ZF Sachs AG Multiple clutch device

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WO2003102438A1 (en) 2003-12-11
US20050139023A1 (en) 2005-06-30
KR20050005496A (en) 2005-01-13
DE10223780C1 (en) 2003-10-16
KR100901608B1 (en) 2009-06-08
JP4473118B2 (en) 2010-06-02
EP1511947B1 (en) 2010-03-03
EP1511947A1 (en) 2005-03-09
US7147095B2 (en) 2006-12-12
DE50312478D1 (en) 2010-04-15
JP2005527758A (en) 2005-09-15

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